EP1356203B1 - Dispositif pour alimenter un moteur a combustion interne en carburant sous haute pression - Google Patents

Dispositif pour alimenter un moteur a combustion interne en carburant sous haute pression Download PDF

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Publication number
EP1356203B1
EP1356203B1 EP01991686A EP01991686A EP1356203B1 EP 1356203 B1 EP1356203 B1 EP 1356203B1 EP 01991686 A EP01991686 A EP 01991686A EP 01991686 A EP01991686 A EP 01991686A EP 1356203 B1 EP1356203 B1 EP 1356203B1
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EP
European Patent Office
Prior art keywords
pressure
fuel
longitudinal grooves
bore
valve member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP01991686A
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German (de)
English (en)
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EP1356203A1 (fr
Inventor
Harald Schorr
Alexander Redlich
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1356203A1 publication Critical patent/EP1356203A1/fr
Application granted granted Critical
Publication of EP1356203B1 publication Critical patent/EP1356203B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies

Definitions

  • the invention is based on a device for high-pressure fuel supply of an internal combustion engine, as it corresponds to the preamble of patent claim 1.
  • a device for high-pressure fuel supply of an internal combustion engine, as it corresponds to the preamble of patent claim 1.
  • Such a device is in the form of a fuel injection valve, for example from the published patent application DE 198 43 344 A1 known.
  • a bore is formed, in which a piston-shaped valve member is arranged longitudinally displaceable.
  • the valve member has a sealing portion with which it is guided in a guide portion of the bore, so that in this area between the valve member and the inner wall of the bore only a very small annular gap remains just large enough to ensure the longitudinal displacement of the valve member ,
  • At the combustion chamber facing the end of the guide portion of the bore is followed by a trained by a radial extension of the bore pressure chamber to the guide area, which pressure chamber can be filled with fuel under high pressure.
  • the pressure chamber continues to the combustion chamber as an annular channel surrounding the valve member and is delimited at the combustion chamber end by a valve sealing surface which closes the bore toward the combustion chamber.
  • the valve member has at its combustion chamber end a valve sealing surface which cooperates with the valve seat for controlling at least one injection opening, so that the injection opening can be connected to the pressure chamber by the longitudinal movement of the valve member.
  • a leakage oil space adjoins it, which is constantly kept at a low pressure level by a corresponding leak oil connection. Since at least during the injection in the pressure chamber, a very high fuel pressure is applied, there is a high pressure difference between the two ends of the guide portion of the bore. As a result, fuel is forced through the annular gap, which remains due to the L Lucassverschiebles between the sealing portion of the valve member and the guide portion of the bore from the pressure space in the leakage oil space. Especially in the case of fuels such as are used for self-igniting internal combustion engines, the fuel in this area also serves to lubricate the valve member in the bore.
  • the document DE 198 20 264 shows recesses on the valve needle, which have the shape of fine grooves. These run transversely to the longitudinal axis of the valve needle, parallel to this or at an angle thereto. Specifically, the longitudinal grooves extend over the entire, guided length of the valve needle, so that the longitudinal grooves are always connected to the pressure chamber and reach into a low-pressure space.
  • the inventive device for high-pressure fuel supply of an internal combustion engine has the advantage that at the guide portion of the guided in the bore piston-shaped element recesses are formed which are hydraulically connected to the pressure chamber, but do not reach into the leakage oil space.
  • the recesses are in this case preferably formed as grooves, which lead from the high pressure region, so the pressure chamber, up to a certain height of the sealing portion, but not into the low pressure region.
  • the structure of the recesses not only prevents the pressure drop behind the narrowest point of the annular channel formed between the piston-shaped element and the bore, but builds up a higher pressure compared to the opposite side. This pressure buildup causes the valve member to experience a force that is directed away from the inner wall surface of the bore, thus centering the piston-shaped member in the bore again.
  • the recesses are arranged distributed uniformly over the circumference of the piston-shaped element, so as to connect each area of the circumference of the piston-shaped element via a recess with the pressure chamber.
  • the leakage flow does not increase excessively through the annular gap between the piston-shaped element and the bore through the recesses, the cross section of the recesses must be very small.
  • This is in the inventive Device provided a depth of 1 to 50 microns, preferably 2 to 10 microns.
  • the width can vary between 100 and 500 microns.
  • the formation of the recesses according to the invention when the device is a fuel injection valve and the piston-shaped element is a valve member. Due to the high fuel pressures in such fuel injectors, as are preferably used for auto-ignition internal combustion engines, an exact alignment of the valve member in the bore is particularly important to ensure proper operation over the life.
  • FIG. 1 a longitudinal section through a fuel injection valve, the FIGS. 2, 3, 4 and 5 Magnifications in the guide area of the valve member.
  • FIG. 1 is a longitudinal section through a device for high-pressure fuel supply of an internal combustion engine, wherein the device is here a fuel injection valve.
  • a designed as a valve body 1 component has a bore 3, in which a piston-shaped element, which is designed here as a valve member 5, longitudinally displaceable is arranged.
  • the valve member 5 has a longitudinal axis 6 and is sealingly guided with a sealing portion 105 in a guide chamber 103 facing away from the combustion chamber of the bore 3. Starting from the sealing portion 105 of the valve member 5, the valve member 5 tapers to the combustion chamber to form a pressure shoulder 13 and thus passes over into a valve member shaft 205 reduced in diameter.
  • a valve sealing surface 7 is formed, which is at least approximately conical and cooperates with a formed on the combustion chamber end of the bore 3 valve seat 9.
  • at least one injection opening 11 is formed, which connects the bore 3 with the combustion chamber of the internal combustion engine.
  • a pressure chamber 19 is formed by a radial extension of the bore 3 in the valve body 1, which extends as a valve member 205 surrounding the annular channel to the valve seat 9.
  • the pressure chamber 19 is connectable via an inlet channel 25 extending in the valve body 1 with a high-pressure fuel source, not shown in the drawing, and can be filled with fuel at high pressure via this.
  • the combustion chamber facing away from the end face of the valve body 1 abuts against a valve holding body 2 and is clamped against it by a tensioning device, not shown in the drawing in the axial direction. It can also be provided to form the valve body 1 and the valve holding body 2 in one piece.
  • a leakage oil chamber 15 is formed, in which the bore 3 opens and which is constantly relieved of pressure via a drain channel, not shown in the drawing, so that there is always a low fuel pressure in the leakage oil chamber 15.
  • a closing device not shown in the drawing is arranged, which exerts a closing force F on the valve member 5, wherein the closing force F directed to the valve seat 9 is.
  • the direction of the closing force F is indicated in the drawing by an arrow.
  • the function of the fuel injection valve in the injection of fuel into the combustion chamber of the internal combustion engine is as follows, wherein two modes of operation can be distinguished: In the first mode, a high fuel pressure in the pressure chamber 19 is constantly maintained by the high-pressure fuel source via the inlet channel 25. This results in a hydraulic force on the pressure shoulder 13, which is directed against the closing force F. If no injection takes place, then the closing force F is selected to be correspondingly high, so that the valve member 5 bears against the valve seat 9 with its valve sealing surface 7. If an injection takes place, then the closing force F is reduced so that the hydraulic force on the pressure shoulder 13 now predominates and the valve member 5 is moved in the direction of the leakage oil space 15.
  • valve sealing surface 7 lifts off from the valve seat 9 and fuel is injected from the pressure chamber 19 through the injection opening 11 into the combustion chamber of the internal combustion engine.
  • closing force F By a corresponding increase in the closing force F, the injection is terminated again and the valve member 5 returns to its original position by a longitudinal movement.
  • an at least approximately constant closing force is exerted on the valve member 5, and the movement of the valve member 5 is effected by a variable fuel pressure in the pressure chamber 19. If no injection takes place, then prevails in the pressure chamber 19, a lower fuel pressure, so that the hydraulic force on the pressure shoulder 13 is smaller than the closing force F. If an injection takes place, then fuel is introduced via the inlet channel 25 into the pressure chamber 19, whereby there the fuel pressure increases.
  • the valve member 5 moves in the longitudinal direction and lifts, as in the first mode, with the valve sealing surface 7 from the valve seat 9, and the injection is carried out as described in the first mode.
  • the end of the injection is initiated by the fuel supply is interrupted by the supply passage 25, whereby the fuel pressure in the pressure chamber 19 drops and thus the hydraulic force on the pressure shoulder 13. Due to the closing force F, the valve member 5 returns to the starting position and closes the injection port 11.
  • FIG. 2 an enlarged view in the region of the guide portion 103 of the bore 3 is shown.
  • the valve member 5 is longitudinally displaceable in the bore 3, it must there have a certain play, so that between the seal portion 105 of the valve member 5 and the guide portion 103 of the bore 3, an annular gap 17 is formed.
  • the pressure chamber 19 is always applied a high fuel pressure
  • constantly fuel flows through this annular gap-shaped throttle gap from the pressure chamber 19 into the leakage oil chamber 15.
  • the fuel pressure drops in the throttle gap 17 approximately linearly from the pressure chamber 19 to the leakage oil chamber 15 down from.
  • valve member 5 undergoes a rotationally symmetrical hydraulic force on the surface of the sealing portion 105, so that cancel the radial forces on the valve member 5 each other. If the valve member 5, however, shifted from its central position, the annular gap 17 is smaller on the investment side, while it increases correspondingly on the opposite side. Without consideration of the recesses 30, the pressure in the annular gap 17 drops at least approximately linearly from the high-pressure chamber 19 to the leakage oil chamber 15. Considering the groove-shaped recesses 30, as they FIG. 2 shows, there is another state: The plant side of the valve member 5 opposite flows through the enlarged annular gap 17 there, the main portion of the leakage past the valve member 5.
  • FIG. 3 shows the same section as FIG. 2 a further fuel injection valve according to the invention.
  • the recesses 30 are formed here as inclined to the longitudinal axis 6 longitudinal grooves so that they have a helical course.
  • Another embodiment is shown in FIG.
  • the recesses 30 are shown as meandering grooves extending to about two thirds of the length of the sealing portion 105 of the valve member 5.
  • FIG. 5 a further embodiment is shown in which the recesses 30 are formed by piecewise straight grooves which are hydraulically connected to each other. This results in labyrinth-like structures on the surface of the valve member 5, the uniform distribution of the fuel over the Ensure the circumference of the valve member 5 without a preferential direction exists.
  • FIGS. 2, 3, 4 and 5 develop their respective advantage only in the overall geometry of the fuel injection valve. Which configuration, depth and cross-sectional shape is particularly advantageous in each case must be determined by experiment or simulation of the airfoil.
  • the cross-section of the recesses 30 must be kept relatively small.
  • the recesses 30 have a depth of 1 to 50 ⁇ m, preferably 2 to 10 ⁇ m.
  • the width of the groove-shaped recesses 30 is preferably 100 to 500 microns, wherein the cross-sectional shape of the recesses may be formed, for example, rectangular, circular section, triangular or U-shaped.
  • the recesses extend, starting from the combustion chamber facing the end of the sealing portion 105, about half to about three quarters of the length of the sealing portion 105. In this way, the leakage oil flow flowing through the recesses 30 and from there through the annular gap 17 to the leakage oil chamber 15, kept within reasonable limits.
  • recesses 30 In addition to the application of the recesses 30 according to the invention on a valve member 5, it may also be provided to form such recesses on other piston-shaped elements which are longitudinally displaceably guided in a bore, if on one side of the bore a high pressure and on the other side a low pressure prevails.
  • Such an arrangement is also given for example in fuel injection pumps, which compress fuel on one side by a longitudinally movable piston which is mounted in a bore and supply under high pressure to a fuel injection valve, while on the other side of the guide portion of this piston, a low fuel pressure is maintained.
  • the recesses 30 according to the invention are not formed on the piston-shaped element 5, but on the inner wall of the bore 3. Hydraulically, this results in a comparable situation as in the formation of the recesses 30 on the outer surface of the piston-shaped element 5.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne un dispositif pour alimenter un moteur à combustion interne en carburant sous haute pression, ce dispositif comprenant un élément (5) en forme de piston, longitudinalement mobile dans l'alésage (3) d'une pièce (1). Cet élément (5) en forme de piston est guidé au niveau d'une partie étanchéité (105) dans une partie guidage (103) de l'alésage (3), cette partie guidage (103) débouchant à une extrémité dans une chambre de pression (19) se remplissant de carburant sous haute pression et à l'autre extrémité dans une chambre de trop-plein (15). La partie étanchéité (105) de l'élément (5) en forme de piston comporte au moins un évidement (30) en liaison hydraulique avec la chambre de pression (19). A part l'interstice annulaire (17) façonné entre l'élément (5) en forme de piston et la paroi intérieure de la partie guidage (103), cet évidement est étanché relativement à la chambre de trop-plein (15), ce qui permet à l'élément (5) en forme de piston d'être hydrauliquement centré dans l'alésage (3).

Claims (7)

  1. Soupape d'injection de carburant pour l'alimentation en carburant à haute pression d'un moteur à combustion interne, comprenant un organe de soupape (5) qui est disposé de manière déplaçable longitudinalement dans un alésage (3) d'un corps de soupape (1), et lequel organe de soupape (5) est guidé avec une portion d'étanchéité (105) dans une portion de guidage (103) de l'alésage (3), la portion de guidage (103) débouchant à une extrémité dans un espace de pression (19) pouvant être rempli de carburant haute pression, et à l'autre extrémité dans un espace de fuite d'huile (15) dans lequel espace de fuite d'huile (15) règne toujours une pression de carburant inférieure, caractérisée en ce que sur la portion d'étanchéité (105) de l'organe de soupape (5) sont réalisées des gorges longitudinales (30) s'étendant dans la direction longitudinale de l'organe de soupape (5), lesquelles sont connectées hydrauliquement à l'espace de pression (19) et à leur extrémité tournée vers l'espace de pression (19) s'étendent jusque dans l'espace de pression (19) mais pas jusque dans l'espace de fuite d'huile (15), et lesquelles sont étanchées vis-à-vis de l'espace de fuite d'huile (15) à l'exception de l'interstice annulaire (17) réalisé entre l'organe de soupape (5) et la paroi interne de la portion de guidage (103), les gorges longitudinales (30) présentant une profondeur de 2 à 50 µm.
  2. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce que les gorges longitudinales (30) présentent une section transversale de forme rectangulaire.
  3. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce que les gorges longitudinales (30) présentent une section transversale triangulaire.
  4. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce que les gorges longitudinales (30) présentent une section transversale en forme de portion de cercle.
  5. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce que les évidements s'étendent sur 20 % à 80 % de la longueur de la portion d'étanchéité (105) de l'organe de soupape (5), de préférence sur 50 à 80 %.
  6. Soupape d'injection de carburant selon l'une quelconque des revendications précédentes, caractérisée en ce que les gorges longitudinales (30) présentent une profondeur de 2 à 10 µm.
  7. Soupape d'injection de carburant selon l'une quelconque des revendications précédentes, caractérisée en ce que plusieurs gorges longitudinales (30) sont réalisées sur l'organe de soupape (5), lesquelles sont réparties uniformément sur la périphérie.
EP01991686A 2001-01-19 2001-12-22 Dispositif pour alimenter un moteur a combustion interne en carburant sous haute pression Expired - Lifetime EP1356203B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10102234A DE10102234A1 (de) 2001-01-19 2001-01-19 Vorrichtung zur Kraftstoff-Hochdruckversorgung einer Brennkraftmaschine
DE10102234 2001-01-19
PCT/DE2001/004915 WO2002064969A1 (fr) 2001-01-19 2001-12-22 Dispositif pour alimenter un moteur a combustion interne en carburant sous haute pression

Publications (2)

Publication Number Publication Date
EP1356203A1 EP1356203A1 (fr) 2003-10-29
EP1356203B1 true EP1356203B1 (fr) 2011-09-28

Family

ID=7671029

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01991686A Expired - Lifetime EP1356203B1 (fr) 2001-01-19 2001-12-22 Dispositif pour alimenter un moteur a combustion interne en carburant sous haute pression

Country Status (6)

Country Link
US (1) US7011256B2 (fr)
EP (1) EP1356203B1 (fr)
JP (1) JP2004518076A (fr)
DE (1) DE10102234A1 (fr)
PL (1) PL357212A1 (fr)
WO (1) WO2002064969A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10245573A1 (de) * 2002-09-27 2004-04-08 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
JP4007202B2 (ja) 2003-01-23 2007-11-14 株式会社デンソー 軸部材の摺動構造およびインジェクタ
JP4119812B2 (ja) * 2003-09-19 2008-07-16 ボッシュ株式会社 燃料噴射弁
JP4066959B2 (ja) * 2004-01-27 2008-03-26 株式会社デンソー 燃料噴射装置
JP2008057458A (ja) * 2006-08-31 2008-03-13 Mitsubishi Heavy Ind Ltd 燃料噴射弁
DE102012223334A1 (de) * 2012-12-17 2014-06-18 Robert Bosch Gmbh Kolbenzylindereinheit
DE102014218179A1 (de) 2014-09-11 2016-03-17 Robert Bosch Gmbh Axialkolbenmaschine und Verwendung einer Axialkolbenmaschine
DE102015211705A1 (de) * 2015-06-24 2016-12-29 Robert Bosch Gmbh Kraftstoffinjektor mit Steuerventil
DE102015226326A1 (de) * 2015-12-21 2017-06-22 Robert Bosch Gmbh Hydraulische Kopplereinrichtung und Kraftstoffeinspritzventil mit einer solchen
DE102017115613A1 (de) * 2017-07-12 2019-01-17 L'orange Gmbh Kraftstoffinjektor und Einspritzsystem für eine Brennkraftmaschine

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3433710A1 (de) * 1984-09-14 1986-03-27 Robert Bosch Gmbh, 7000 Stuttgart Elektrisch gesteuerte pumpeduese fuer die kraftstoffeinspritzung bei dieselbrennkraftmaschinen
DE19820264A1 (de) 1998-05-07 1999-11-11 Mtu Friedrichshafen Gmbh Hochdruck-Kolbenzylindereinheit
GB9819746D0 (en) * 1998-09-11 1998-11-04 Lucas Ind Plc Fuel injector
DE19843344A1 (de) * 1998-09-22 2000-03-23 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
US6776358B2 (en) * 1998-10-09 2004-08-17 Jun Arimoto Fuel injection nozzle for a diesel engine
WO2000022295A1 (fr) 1998-10-09 2000-04-20 Jun Arimoto Valve d'injection de carburant pour moteur diesel
GB9904938D0 (en) * 1999-03-04 1999-04-28 Lucas Ind Plc Fuel injector

Also Published As

Publication number Publication date
WO2002064969A1 (fr) 2002-08-22
PL357212A1 (en) 2004-07-26
US20040124286A1 (en) 2004-07-01
DE10102234A1 (de) 2002-07-25
JP2004518076A (ja) 2004-06-17
EP1356203A1 (fr) 2003-10-29
US7011256B2 (en) 2006-03-14

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